US6928995B1 - Emission control valve having improved force-balance and anti-coking - Google Patents
Emission control valve having improved force-balance and anti-coking Download PDFInfo
- Publication number
- US6928995B1 US6928995B1 US10/785,306 US78530604A US6928995B1 US 6928995 B1 US6928995 B1 US 6928995B1 US 78530604 A US78530604 A US 78530604A US 6928995 B1 US6928995 B1 US 6928995B1
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- United States
- Prior art keywords
- seat
- valve
- frustoconical surface
- surface zone
- seats
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
- 238000004939 coking Methods 0.000 title description 4
- 238000004519 manufacturing process Methods 0.000 claims abstract description 7
- 238000002485 combustion reaction Methods 0.000 claims description 11
- 230000003134 recirculating effect Effects 0.000 claims 1
- 239000007789 gas Substances 0.000 description 20
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 4
- 238000010276 construction Methods 0.000 description 4
- 239000000463 material Substances 0.000 description 4
- 238000013459 approach Methods 0.000 description 3
- 238000013461 design Methods 0.000 description 3
- 239000002184 metal Substances 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 239000000470 constituent Substances 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 229910052757 nitrogen Inorganic materials 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000011217 control strategy Methods 0.000 description 1
- 238000000151 deposition Methods 0.000 description 1
- 230000001627 detrimental effect Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 230000008520 organization Effects 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 230000011664 signaling Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/65—Constructional details of EGR valves
- F02M26/66—Lift valves, e.g. poppet valves
- F02M26/69—Lift valves, e.g. poppet valves having two or more valve-closing members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/38—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with two or more EGR valves disposed in parallel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/52—Systems for actuating EGR valves
- F02M26/53—Systems for actuating EGR valves using electric actuators, e.g. solenoids
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/11—Manufacture or assembly of EGR systems; Materials or coatings specially adapted for EGR systems
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/40—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with timing means in the recirculation passage, e.g. cyclically operating valves or regenerators; with arrangements involving pressure pulsations
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/65—Constructional details of EGR valves
- F02M26/66—Lift valves, e.g. poppet valves
- F02M26/67—Pintles; Spindles; Springs; Bearings; Sealings; Connections to actuators
Definitions
- This invention relates generally to emission control valves that are used in emission control systems associated with internal combustion engines in automotive vehicles.
- the invention particularly relates to force-balance and anti-coking improvements in exhaust gas recirculation (EGR) valves.
- EGR exhaust gas recirculation
- Controlled engine exhaust gas recirculation is a known technique for reducing oxides of nitrogen in products of combustion that are exhausted from an internal combustion engine to atmosphere.
- a typical EGR system comprises an EGR valve that is controlled in accordance with engine operating conditions to regulate the amount of engine exhaust gas that is recirculated to the fuel-air flow entering the engine for combustion so as to limit the combustion temperature and hence reduce the formation of oxides of nitrogen.
- EGR valves are subject to harsh operating environments that include wide temperature extremes and vibrations. Tailpipe emission requirements impose stringent demands on the control of such valves.
- An electric actuator such as a solenoid that includes a sensor for signaling position feedback to indicate the extent to which the valve is open, can provide the necessary degree of control when properly controlled by the engine control system.
- An EGR valve that is operated by an electric actuator is often referred to as an EEGR valve.
- an engine with which an EEGR valve is used is a diesel engine
- further considerations bear on the valve. Because such engines may generate significantly large pressure pulses, attainment of acceptable control may call for the use of a force-balanced EEGR valve so that any influence of exhaust gas pressure on valve control is minimized, and ideally completely avoided. For example, a large pressure pulse should not be allowed to force open an EEGR valve that is being operated to closed position by the solenoid.
- a double-pintle type valve can endow an EEGR with a degree of force balance that is substantial enough to minimize the influence of exhaust gas pressure on valve control, for example minimizing the risk that large exhaust pressure pulses will open the EEGR valve when the engine control strategy is calling for the valve to be closed.
- a double-pintle type valve allows the valve to have a split-flow path where each pintle is associated with a respective valve seat. Such a valve can handle larger flow rates with a degree of control suitable for control of EGR.
- Certain combustion products in engine exhaust gases may tend to deposit on certain surfaces of certain parts of an EEGR valve. This phenomenon is sometimes called “coking”, and it can be detrimental to valve performance.
- the present invention relates to certain improvements in the construction of an EEGR valve, such as a double-pintle EEGR valve, particularly improvements in the pintle-seat interfaces.
- One improvement is directed to an interface that tends to discourage the deposit of materials from the exhaust gases passing through the valve on surfaces at the interface so that proper performance of an EEGR valve can continue during its useful life free of deposits at the interface that might otherwise seriously impair acceptable valve performance.
- Another improvement is directed to better force-balancing of the pintle in a double-pintle EEGR valve for minimizing the influence of exhaust pressure fluctuations on valve operation.
- the conjunction of these improvements in an EEGR valve can contribute to better valve performance and longer useful life of an EEGR valve in an exhaust emission control system of a diesel engine, and with cost-effectiveness.
- a general aspect of the invention relates to an emission control valve for use in an emission control system of an internal combustion engine.
- the valve comprises valve body structure providing an inlet port at which flow enters the valve and an outlet port at which flow exits the valve.
- a valve element comprises first and second closures spaced apart along an axis for respective cooperation with respective seats that are axially spaced apart to selectively seat on the respective seat for disallowing flow between the inlet port and the outlet port and to unseat from the respective seat for allowing flow between the inlet port and the outlet port.
- An actuator selectively positions the valve element along the axis relative to the seats.
- Each seat circumscribes a respective through-hole for flow.
- the through-hole of one seat is large enough diametrically to allow the closure that seats on the other seat to pass through during fabrication of the valve.
- Each through-hole comprises a respective frustoconical surface zone coaxial with the axis and tapered in the same axial direction.
- the closure that seats on the other seat seats on a radially outermost portion of the frustoconical surface zone of the through-hole of the other seat when the valve element is disallowing flow, and the other closure seats on a radially innermost portion of the frustoconical surface zone of the through-hole of the one seat when the valve is disallowing flow.
- Another general aspect relates to an exhaust gas recirculation system having such a valve.
- FIG. 1 is an elevation view of an EEGR valve embodying principles of the invention.
- FIG. 2 is a left side elevation view of FIG. 1 .
- FIG. 3 is an enlarged cross section view in the direction of arrows 3 — 3 in FIG. 1 .
- FIG. 4 is an elevation view of one part of the valve by itself, that part being a double-pintle.
- FIG. 5 is a cross section view in the direction of arrows 5 — 5 in FIG. 3 .
- FIG. 6 is an elevation view of another part of the valve by itself, that part being a seat element having a double-seat.
- FIG. 7 is a right side elevation view of FIG. 6 .
- FIG. 8 is a rear elevation view of FIG. 6 .
- FIG. 9 is a top plan view of FIG. 8 .
- FIG. 10 is a cross section view in the direction of arrows 10 — 10 in FIG. 8 , but including the pintle.
- FIG. 11 is an enlarged fragmentary view of a portion of FIG. 10 showing a modification.
- FIG. 12 is an enlarged fragmentary view of another portion of FIG. 10 showing a modification.
- FIGS. 1–3 illustrate the general arrangement and organization of an exemplary EEGR valve 20 embodying principles of the present invention.
- Valve 20 comprises a base 22 and an elbow 24 assembled together to form a flow path 26 through the valve between an inlet port 28 provided in a flange at a side of base 22 and an outlet port 30 provided in a flange at one end of elbow 24 .
- Base 22 is a metal part that has a main longitudinal axis 32 .
- Base 22 may be considered to have a generally cylindrical shape about axis 32 comprising a generally cylindrical wall bounding an interior space that is open at opposite axial end faces of the base.
- Base 22 is constructed so that its interior space is also open to inlet port 28 .
- An end of elbow 24 that is opposite the end containing outlet port 30 is fastened in a sealed manner to the lower end face of base 22 so that the interior of elbow 24 is open to the interior space of base 22 .
- a cover 34 is fastened in a sealed manner to the upper end face of base 22 to close that end of the interior space of base 22 while providing a platform for the mounting of an electric actuator 36 on the exterior of the cover.
- Actuator 36 comprises a solenoid that, when the valve is installed on an engine in a motor vehicle, is electrically connected via an electric connector 38 (shown out of position in FIG. 3 ) to an electrical system of the motor vehicle to place the valve under the control of an engine controller in the vehicle.
- a bearing 40 is centrally fit to cover 34 such that a guide bore of the bearing is coaxial with axis 32 .
- Bearing 40 serves to axially guide a double-pintle 42 (shown by itself in FIG. 4 ) of valve 20 along axis 32 via a guiding fit of the bearing guide bore to an upper portion of a stem 44 of double-pintle 42 that extends completely through the bearing guide bore from an armature of the solenoid into the interior space of base 22 where upper and lower pintles 46 , 48 are disposed on stem 44 .
- a double-seat element 50 shown by itself in FIGS. 6–9 is fit to base 22 within the latter's interior space.
- Element 50 is a machined metal part that has a generally cylindrical shape. It comprises a generally cylindrical wall 52 that is coaxial with axis 32 in valve 20 and that is open at opposite axial ends.
- Element 50 comprises axially spaced apart upper and lower seats 54 , 56 (see FIG. 10 ) with which pintles 46 , 48 respectively cooperate.
- Wall 52 comprises two pairs of openings, or apertures: an upper pair 58 , 60 , and a lower pair 62 , 64 .
- the lower pair are arranged axially between seats 54 , 56 to provide for the open interior of element 50 that is circumscribed by wall 52 between seats 54 , 56 to communicate through the opening in base 22 to inlet port 28 .
- the upper pair 58 , 60 are arranged axially beyond seat 54 relative to the lower pair 62 , 64 to provide for the open interior of element 50 that is circumscribed by wall 52 beyond upper seat 54 to communicate with respective entrances to an internal passageway 66 (see FIG. 5 ) than runs within base 22 internally through a portion of the generally cylindrical wall of the base that is in the semi-circumferential portion of that wall opposite inlet port 28 .
- the outside diameter surface of wall 52 is stepped, comprising zones of successively larger diameter from bottom to top so as to allow element 50 to be assembled to base 22 by inserting element 50 into the interior space of base 22 through the opening in the upper end face of the base.
- the smallest outside diameter zone of wall 52 is at the bottom of element 50 essentially coextensive with seat 56 .
- the next larger diameter zone is the one containing apertures 62 , 64 , and at the juncture of those two zones is a chamfered shoulder 68 .
- the next larger diameter zone is the one containing apertures 58 , 60 , and at its juncture with the zone containing apertures 62 , 64 , there is a raised circular ridge 70 having an inclined surface 72 that wedges with a portion of the inside diameter of the cylindrical wall of base 22 when element 50 is assembled to the base.
- the uppermost zone of wall 52 comprises a circular lip 76 on the outside and a shoulder on the inside.
- each of the two pintles 46 , 48 seats on a respective seat, closing the respective opening, or through-hole, circumscribed by the respective seat.
- the armature is spring-biased to urge the pintles against the seats with an appropriate amount of force.
- upper pintle 46 is less than that of the through-hole circumscribed by lower seat 56 so that the former can pass through the latter during assembly of the double-pintle into the valve. Thereafter elbow 24 is fastened to base 22 to complete the assembly.
- Valve is substantially force-balanced because of the particular double-pintle design.
- inlet port 28 When inlet port 28 is communicated to the engine exhaust system so that hot engine exhaust gases can enter the valve, the pressure of those gases acting on the pintles creates forces that are substantially equal in magnitude, but in opposite directions along axis 32 , although the upward force acting on pintle 48 will have a slightly larger magnitude than the downward one acting on pintle 46 .
- pressure pulses will at most have a very minor, and ideally negligible, effect on the positioning of double-pintle 42 by actuator 36 . This is important for control accuracy.
- a double-pintle valve splits the entering exhaust gas flow so that the flow divides more or less equally as it passes through seat element 50 .
- the circumferential span of the opening in the wall of seat element 50 should be essentially its semi-circumference.
- the seat element is a machined part where the two apertures 62 , 64 are separated by a narrow axial bar 80 in the wall, rather than being a single aperture having a like semi-circumferential span. Similarly, apertures 58 , 60 are separated by a somewhat wider bar 84 .
- FIG. 10 shows the closed condition with each pintle 46 , 48 seated on the respective seat 54 , 56 .
- Seat 54 circumscribes a circular through-hole defined by a circular cylindrical surface zone 54 A both parallel and coaxial with axis 32 and a frustoconical surface zone 54 B that extends from a circular edge 54 C at its junction with zone 54 A coaxial with axis 32 in the direction toward the space circumscribed by wall 52 between the two seats.
- the cone angle of zone 54 B is 30° in this particular embodiment.
- Zone 54 B ends at a flat surface zone 54 D that is perpendicular to axis 32 .
- zones 54 B and 54 D endows the seat with an obtuse-angled circular corner edge 54 E against which a frustoconical surface 46 A of pintle 46 seats when valve 20 is closed.
- Surface 46 A has a cone angle of 42° in this particular embodiment.
- Seat 56 circumscribes a circular through-hole defined by a circular cylindrical surface zone 56 A both parallel and coaxial with axis 32 and a frustoconical surface zone 56 B that extends from an obtuse-angled circular corner edge 56 C at its junction with zone 56 A coaxial with axis 32 in the direction away from the space circumscribed by wall 52 between the two seats.
- Zone 56 B ends at a flat surface zone 56 D that is perpendicular to axis 32 .
- the cone angle of zone 56 B is 60° in this particular embodiment.
- a frustoconical surface 48 A of pintle 48 seats on corner edge 56 C when valve 20 is closed.
- Surface 48 A has a cone angle of 42° in this particular embodiment.
- the diameter of zone 56 A is made larger than the largest outside diameter of pintle 46 , with an appropriate amount of radial clearance to facilitate assembly.
- the largest outside diameter of pintle 46 occurs in a circular cylindrical portion that extends axially from frustoconical surface 46 A.
- the obtuse-angled corner edge 54 E at the junction of seat surface zones 54 B, 54 d makes essentially circular line edge contact with surface 46 A of pintle 46
- the obtuse-angled corner edge 56 C at the junction of seat surface zones 56 A, 56 B makes essentially circular line edge contact with surface 48 A of pintle 48 .
- FIGS. 11 and 12 show respective modifications to seats 54 and 56 in another example.
- the drawings are exaggerated for clarity of illustration.
- Edge 54 E has a slight chamfer 54 F instead of being sharp.
- the cone angle of the chamfer is slightly larger (1° larger in the example) than the cone angle of surface 46 A.
- edge 56 C has been modified to includes a slight chamfer 54 E, whose cone angle is also 1° larger than the cone angle of surface 48 A. It is believed that the inclusion of the chamfers can improve durability and performance.
- Anti-coking features are embodied in the pintle-seat interfaces because of the geometries that have been described.
- the valve When the valve is operated just slightly open, the flow is increasingly constricted as it approaches the corner edge. Once past the corner edge, the flow is allowed to expand due to the angular relationship between the seat and pintle surface zones.
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- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
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- Lift Valve (AREA)
Abstract
Description
Claims (12)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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US10/785,306 US6928995B1 (en) | 2004-02-24 | 2004-02-24 | Emission control valve having improved force-balance and anti-coking |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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US10/785,306 US6928995B1 (en) | 2004-02-24 | 2004-02-24 | Emission control valve having improved force-balance and anti-coking |
Publications (2)
Publication Number | Publication Date |
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US6928995B1 true US6928995B1 (en) | 2005-08-16 |
US20050183702A1 US20050183702A1 (en) | 2005-08-25 |
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US10/785,306 Expired - Fee Related US6928995B1 (en) | 2004-02-24 | 2004-02-24 | Emission control valve having improved force-balance and anti-coking |
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Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20090183696A1 (en) * | 2008-01-18 | 2009-07-23 | O'flynn Kevin P | Liquid cooling system for internal combustion engine |
US20150276072A1 (en) * | 2014-03-27 | 2015-10-01 | Emerson Process Management Regulator Technologies, Inc. | Double Port Pressure Regulator with Floating Seat |
US20230228331A1 (en) * | 2022-01-19 | 2023-07-20 | Fisher Controls International Llc | Double ported control valves for low flow rate applications |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4350013A (en) * | 1979-02-09 | 1982-09-21 | Nissan Motor Company, Limited | Exhaust gas recirculation system |
US6006732A (en) * | 1998-09-03 | 1999-12-28 | Navistar International Transportation Corp | Balanced flow EGR control apparatus |
US6047690A (en) * | 1997-09-04 | 2000-04-11 | General Motors Corporation | Exhaust gas recirculation valve |
US6247461B1 (en) * | 1999-04-23 | 2001-06-19 | Delphi Technologies, Inc. | High flow gas force balanced EGR valve |
US6279552B1 (en) * | 1998-05-27 | 2001-08-28 | Mitsubishi Denki Kabushiki Kaisha | Exhaust gas re-circulation valve |
US6330880B1 (en) * | 1998-02-27 | 2001-12-18 | Mitsubishi Denki Kabushiki Kaisha | Exhaust gas recirculation system |
-
2004
- 2004-02-24 US US10/785,306 patent/US6928995B1/en not_active Expired - Fee Related
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4350013A (en) * | 1979-02-09 | 1982-09-21 | Nissan Motor Company, Limited | Exhaust gas recirculation system |
US6047690A (en) * | 1997-09-04 | 2000-04-11 | General Motors Corporation | Exhaust gas recirculation valve |
US6330880B1 (en) * | 1998-02-27 | 2001-12-18 | Mitsubishi Denki Kabushiki Kaisha | Exhaust gas recirculation system |
US6279552B1 (en) * | 1998-05-27 | 2001-08-28 | Mitsubishi Denki Kabushiki Kaisha | Exhaust gas re-circulation valve |
US6006732A (en) * | 1998-09-03 | 1999-12-28 | Navistar International Transportation Corp | Balanced flow EGR control apparatus |
US6247461B1 (en) * | 1999-04-23 | 2001-06-19 | Delphi Technologies, Inc. | High flow gas force balanced EGR valve |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20090183696A1 (en) * | 2008-01-18 | 2009-07-23 | O'flynn Kevin P | Liquid cooling system for internal combustion engine |
US20150276072A1 (en) * | 2014-03-27 | 2015-10-01 | Emerson Process Management Regulator Technologies, Inc. | Double Port Pressure Regulator with Floating Seat |
US9354638B2 (en) * | 2014-03-27 | 2016-05-31 | Emerson Process Management Regulator Technologies, Inc. | Double port pressure regulator with floating seat |
US20230228331A1 (en) * | 2022-01-19 | 2023-07-20 | Fisher Controls International Llc | Double ported control valves for low flow rate applications |
US11719345B1 (en) * | 2022-01-19 | 2023-08-08 | Fisher Controls International Llc | Double ported control valves for low flow rate applications |
Also Published As
Publication number | Publication date |
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US20050183702A1 (en) | 2005-08-25 |
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